Progressive change-speed device



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Feb. 1 1.927.

EsNAULT-PE LTERlE PROGRESSIVE CHANGE SPEED DEVICE 9 Shets-Sheet 4 Filed June 4. 1925 T mw mm P aM m NWW s E T a E m 0v v HS.

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R. ESNAULT-PELTERIE PROGRESSIVE CHANGE SPEED DEVICE Filed June 4. 1925 9 Sheets-Sheet '7 x W W 2 I-ns A'r'roaNsv 1,616,311 1 1927' R. ESNAULT-PELTERBE PROGRESSIVE CHANGE SPEED DEVICE Filed June 4. 1925 9 Sheets-Sheet 8 Patented Feb. 1, 1927.

UNITED STATES ROBERT ESNAULT-PELTERIE, OF BOULOGNE-SUR-SEINE, FRANCE.

PROGRESSIVE CHANGE-SPEED DEVICE. v

Application filed June 4, 1925, Serial No. 34,855, and in France June 10, 1924.

My invention relates to a change-speed device of a progressive nature wherein the rollers, which are formed by surfaces of revolution and are symmetrical with reference to their equatorial plane, are adapted to roll, without escaping in sliding, upon two pairs of disks which are revoluble upon the main centre line of the apparatus, the two disks of a given pair being angularly connected together, and one of the pairs being angularly connected with the main driving shaft whilst the other pair is angularly connected with the actuated shaft, the speed being changed by the longitudinal variation of the distance between the disks of a given pair, thereby changing the ratio of the speeds of the driving and the actuated shafts.

. Figs. 1 to Gare diagrams showing the distribution of the efforts in my said device.

Figs. 7 to 12 show a simple constructional form of change-speed device.

Fig. 7 is a lengthwise section.

Fi 8 is asection on the line X -X of Fig? for the left hand part and on the line X X* for the right hand part.

Fig. 9 is a section on the line ZZ of Fig. 8 showing the disposition of the roller.

Fig. 10 is a 360 development of the helical ramps which are shown in end view in Fig. 11, said ramps being mounted on the disks C C and coacting with the rollers carried by the actuated shaft.

Fig. 11 is a section on the line U--U of Fig. 7 showing an end view of the said ramps.

Fig. 12 is a cross section on the line X of Fig. 7 for the right hand part and on the line Il -X for the left hand part. 1

Fig 13 to 16 show various forms of the reversing gearing for motor car use.

Figs. 18 to 20 show modified forms of the transmission rollers of the change-speed device Fig. 7'. I

Fig. 21 shows a device analogous to Fig. 7 but adapted for automatic control.

Fig. 22 is a detail view.

Preliminary statementlhe present preliminary statement has for its object to furnish various explanations concerning the description which follows the same.

Let us consider the system shown in Fig. 1 which consists of four rollers A, B B C which are supposed to roll upon one another without friction. If the lengths of their respective radii are represented by the letters indicated upon this figure, it will be at once observed that the ratio between the angular speeds of the axis w and the axis :22 will be v The roller C may be replaced by the ring C (Fig. 2), and herein the formula for the speed ratio remains the same, the only difference being that the axis a: rotates in the contrary direction to the axis w whereas in Fig. 1 it rotates in the same direction; so

use of this mechanism, it is suflicient that the ratio cox wit shall be variable at will, and the formula shows that to this effect it will suflice that v at least one of the radii in the second term of the equation (1) shall be variable.

The system according to my invention utilizes, instead of the variation of only one of these radii, the simultaneous variation of the two radii and b the radii a and a may remain constant or may be variable. To effect this simultaneous variation of I), andb the system may consist of a tapered roller B (Fig. 3) whose axis g g is parallel to the main axis of symmetry X X and which may approach or recede from the latter while remaining parallel thereto; no lengthwise movement need be given to the tapered roller B.

In these conditions, when the roller-A is longitudinally displaced, for instance to the right, as shown in the dotted lines, the roller B will approach the axis X -X and will thus tend to move out of contact with the ring C. If the latter were urged .to the left by a spring R or by other appropriated means, it would move in this direction while still remaining in contact; should the roller A be moved to the left, all the displacements will he obviously in the inverse direction.

It is thus observed that if the action of the spring R (or appropriated means) is sufiiciently powerful, one may obtain a sufhence between the latter and the roller A,

so that the movement will take place without sliding, and the shaft X may actuate the shaft X after the manner of a set of gearing, but with a speed ratio which is variable at will by the displacement of the roller A.

It is also observed in the figure that in certain positions, and chiefly in the position shown in Fig. 3, the pressing action will set up two forces F F which form a couple and tend to move the axis g 2 out of its position parallel to X X. Due to the small value of the coefficient of friction of two metal pieces in contact, and since no sliding is allowed, these forces F F should be considerable, and examination will at once show that such an apparatus cannot be practically constructed, because the axis y I which usually turns at a high speed, must be mounted in straight or ball bearings of an excessive size.

The member C, as will be noted, should be acted upon by the spring R through the medium of a thrust ball bearing R, since the said spring should abut at its other end against a stationary member, and the tapered roller B must necessarily abut against another thrust ball bearing B capable of withstanding the eflort of the spring.

To complete the device, a third thrust ball bearing must be used, which serves as an abutment (not shown) for the mechanism controlling the lengthwise motion of the roller A. The friction of all these abutments would represent a considerable proportion of the work, 'and chiefly as concerns the abutment for the tapered roller. It is further noted that the said mechanism, whose operation has been indicated in a diagrammatic manner, could not be made the subject of any practical application, and its mechanical efficiency would be very low, even if such an apparatus could be constructed.

In the following considerations, and to avoid complication in the text, only the members resembling B in Fig. 3 will be des ignated as rollers, and the members resembling A and C in the same figure will be designated as main disks.

The speed-reducing devices, i. e. the devices for changing the speed at a constant ratio, and the change-speed devices, i. c. the devices for changing the speed at a variable ratio, whether of the friction, the roller, or the ball type, have been proposed and sometimes experimented since a long time, and were constructed in many forms.

The first-mentioned type has been pro duced recently with a very good efliciency, thus enabling the use of such devices foi practical operations, but with the second type, this is apparently not the case. Hav

ing made particular investigations concerning the latter devices, I observed that while a good efficiency can be had for a given speed ratio and the adjacent speed ratios, it is ex tremely diflicult to obtain the proper efficiency for all the speed ratios which are necessary in the operation of a change-speed box, for instance for motor vehicle use.

To meet this latter necessity, the apparatus must simultaneously fulfill certain conditions which have hitherto been fulfilled only in a separate manner, or incompletely, or not at all, in the various known apparatus, and due to the conditions which may be lacking in each particular case, a given apparatus will fail to work in practice, for instance as set forth by .way of example inthe particu lar device above described.

The conditions which my apparatus fulfills in a simultaneous manner are as follows:

1. The pressure is applied in such manner that it is exercised only between members having a like angular motion, in order to obviate all abutments subjected to the effect of pressure and the resulting loss of power.

Such main disks as have the same angular motion, will be designated as pair of main disks.

2. The aggregate of the forces acting upon a pair of main disks is composed according to a zero force and a couple, which could not be obtained by devices comprising a single roller or a single ball.

In the constructional form hereinafter described, this couple, for one of the pairs, is the power couple, and for the other pair, the receiving couple, with the direction inverted.

3. The forces acting upon a given roller at its various points of contact with the concave disks are composed according to a force which is perpendicular to the axis or roller, passing through this axis, and a conple of zero value.

This condition is more clearly set forth by the following decomposition.

(a) Pressure forces, i.c. components'which are perpendicular to the tangent plane com mom to the two members in contact at each point of contact.

For a given roller, and in all the operatingpositions the aggregate of these forces con.- stitutes system in equilibrium. 1. e., it is composed according to a zero force and a zero couple.

(b) Entraining forces, i e. component; situated at'cach point of contact in the tangent plane above specified.

For a given roller, and in all the operating positions, the aggregate of these forces is composed accordlng to a force perpeudrcular to the axis of this roller and passing through this axis and a zero couple.

4. The tangent planes above specified arc allel as possibleto the main axis of rotation,

in order to reduce to a minimum the componentof pivotation at each point of contact. The emct parallel position cannot be attained, since this would prevent the variation of the speed ratio, as observed in Fig. 3, admitting that the cone is converted into a cylinder.

5. I employ more than threerollers, and preferably more than four, but the pressure is collective and without the use of means for distribution of the forces, so that if one of the rolling surfaces has softer portions which would wear more rapidly, such points will be relievcd beeanse they are somewhat concave, and at this time the other rollers will take up the load.

This condition is quite important as concerns the wear, and it cannot be fulfilled by i the systems for the automatic equalizing of the efforts on each roller nor by the systems without equalizing which comprise three rollers, in which the play between the parts necessarily serves to equalize the ac tion; it is fulfilled very imperfectly by the analogoussystems comprising four rollers,

6. The automatic pressure is not proportional to the couple producing thesame, but

its proportion to the latter varies from one operative position of the apparatus to the other, depending upon the outline of the roller.

Obta'imne nt of these desidemta in any said apparatus.Figs. 4, 5 and 6 are diagrams.

and in the inverse direction.

It is observed in Figs. 4, 5 and 6 that in virtue of the separation of the members C and (l in the aforesaid conditions. and of the constant. direction of the axis K K, the said axis will approach the main axis X-X to a degree depending upon the spacing of the main disks and C and in -\ersel y but inasmuch as the motion of the two main disks C (F is always equal and in the contrary direction, the roller B will not be moved lengthwise.

For this reason. should the disks C and C be urged together by a pressure force,

- they will be separated or brought together by a movement which is the reverse of the movement given to the disks C and c uand will be given at each instant, like the latter disks, displacements which are equal and in .lhe contrary direction.

' In view of the considerations, and admitting that the system is so arranged that the disks C C- are constantly urged together in a suflicient manner to prevent all slipping, or si'dewise sliding, at the points of contact. it will be observed (for instance in Fig. 4) that the ratio between the angular speed of the outer. disks and that of the inner disks will be In the intermediate position, Fi 3, [2 :5 whence eel (D1.2 a/2 Figs. 4, 5 and 6 show that the values of the different radii are so combined asto produce in Fig. 4:

(03.4 r (715- in Fig. 5:

1 c012 in Fig. 6:

and this will afford variations in the speed ratios between the driving and the actuated shafts which are sufficient for motor "car purposes, and such-ratios may further be augmented.- 7

In the following description, care .mnst be taken that the disks C and (5 effect an antomatic pressure while determining the 1011- Y gitndinal position of the rollers B, and that the positive control used for the spacing of the disks C and C will effect this spac ing while leaving the disks free to assume the longitudinal position which is imparted to them by the rollers B. I

The aforesaid arrangement may be said to represent Fig. 3, in double disposition, and persons skilled in t-heai't will at once observe that the symmetrical form herein ado pted-will obviously comply with the condition y 3 above mentioned.

By the use of a pair of driving disks C, (1 and a pair of actuated disks C (7,, conditions 1 and can further be realized. (onditious '4 and 5' are also complied with. The mechanical element complying with coildition ti is not shown in the three figure lhacrz'plion off/1c first form of coast/ um How-Figs. 7 to 12 show a simple forn'i of construction of the apparatus.

Fig. 7 isa lengthwise section. Fig. 8 is :1 section on the line X f of Fig. 'T-for the left hand part and on the line X X for the right hand part. Fig. 9 is a section on the line Z-Z of Fig. 8, showing the arrangement of the roller. Fig. 10 is a development on 360 of the helical ramps r referred to.

'which are shown in end view in Fi 11,

for the centering bf'all the rotating parts,

and is centered 1n turn at its inner ends a in a ball bearing g which will be'further The said shaft has for its object to rotate the pair of tempered and rectified steel disks C G The disk C 'is driven directly, through the medium of the balls at serving the purpose of a-key and disposed half in the groove 6 in the main shaft a and half in the groove 7 in the element 0 carried by the disk C the said element actuates, by like means comprising the balls d (ofwhich no further description need be given), the, element 0 which is carried by the disk G A In this manner the disks C C are ro- 'tated by the main shaft, as stated, but they are free to move lengthwise on the shaft in J virtue of the longitudinal play between the balls 3 and d and the ends of their recesses.

are screw threaded in contrary. directions and respectively engage like screwthreaded portions formed in the element 2'. The use of this disposition will be further set forth under the heading of fOperation.

Upon the disks (L C are revolubly mounted a u plurality of double tapered members forming the rollers B; each roller is revoluble on its axis k in the ball bears ings l l which afford a certain lengthwise play relatively to the axis k whose utility .will be explained. under the heading of by the roller m whose axis is secured to the I element 0* and which is slidable lengthwise in the slot n in the cylindrical part of the element 0 this latter is provided with ahelical ramp 0 having an irregular pitch, and the tubular part of-the element a carries a like ramp p. The actuated shaft 1' has mounted thereon an enlarged portion 1 carrying the rollersg Q Q3 g coacting with the said ramps, whereby the actuated shaft 1' will be driven by means of the said ramps and rollers.

' Due to the inclination of'the saidramps,

therewill be obviously produced a length-- wise pressureof the elements F0 0' against the rollers B, depending upon the load couple on the shaft 1'; but the proportion between the couple and the pressure will vary according to .the difi'erentpositions of the parts of the apparatus, i. e. according to the different speed ratios obtained, as will be further set forth.

Fig. 8 is a cross section on the line X X of Fig. 7 for the portion on one side of the centre and on the line X X* for the remaining' portion; Fig. 9 is'a section on the line Z Z of the roller B (Fig. 8) showing the mounting of the axle la of the roller in the fork bracket '8 which is pivoted to a strong axle 25 disposed in an enlargedv part u of the partition 14 traversing the main casing 'v of the apparatus; said bracket allows the roller which it carries to approach or recede from the main shaft 11,-according to the spacing between the disks 0 and C, while remainlng constantly parallel to the axis X X.

Automatic. pressing actz'0n.Fig. 10 is a 360 development of the ramps 0 and 'p,

and shows that the pitch of the ramps increases from the point 1 to the point 2 and is then constant as far as the point 3; when the ramps move according to the arrows, Fig. 10, relatively to the rollers 9 g g, it will be noted that they come nearer to ,each other, and when the rollers attain the point 1,- the mutual pressing action of the two ramps, i. e. the pressing action on the disks 0 G will now be complete, and as above set forth this signifies that the device is in the position of Fig. '4, the ratio being now 1/1.

But when the disks move in the contrary direction, to the arrows Fi 10, they also become separated, and the isks C C will have a like action. When in the position 3, the device will occup in Fig. 6, and the ratio will now be 1/4.

I have found by calculation that for all speeds between the positions 1 and .2, the

the position shown pressing action is preferably proportional to the driving couple, 1. c. it gradually diminishes relatively to the load couple, whence the use of the variable pitch between p'osition'l and position 2. But calculatlon also shows that between the positions 2 and '3 the pressing action should be proportional to the load couple, and this portion oi the developed ramp constitutes a he I conditions would be changed if the rollers is a straight line, i. e. it ix of constantpitch. 'These' had,anoutline different from the double 1 reference to the main centre line of the ap-, paratu's, and it acts upon one of the rollers,

the latter having the diametrical position in order that the resulting pressing efiort shall pass through the main centre line.

Operation.-The operation of the said apparatus is as follows:

The spring R (Fig. 7) urges the two discs 0 and C together; the engine is gradually coupled to the main shaft (1, and the latter will actuate the disks C C which in turn actuate the rollers B and with them the disks C C As soon as the latter are sub- .jected to a resistance from the shaft 1', the

ments 0 .0 are given positive lengthwise movements of a symmetrical nature, in such manner that the rollers B wlll not be subjected to the displacement of said elements,

' but will be radially displaced without longitudinal motion.

This motion of the rollers exclusively in the radial direction can only correspond to longitudinal displacements, equal and contrary, of the inner disks C G and since the latter are connected with the member z' through the medium of screwthreads, equal and contrary, and are unable to rotate on the main shaft, the member I will not be subjected to lengthwise displacements whatever may be the position of the disks C C So, in this device, the angular position of the member '5 relatively to the main shaft is the factor determining the spacing between the disks C 0 this spacing will in turn determine the radial position of the tapered members B; this latter posit-ion determines the spacing between the disks C and C thereby determining the position of the set of rollers 9 upon the respective ramps 0 p, and this latter position will Q finally determine the ratio of. the rece1v-' ing or load couple to the ressing action, whilst the longitudinal position of the set of rollers q will act by successive contacts and in the inverse dierction in orderto determine the longitudinal position of all the parts, and finally the position of the element 2'.

Cont-r01 of the ohaa gsspeed device-elm at the interior with the pinion e keyed to the main shaft a.

\Vhen the ring 2 is stationary, the motion of the planetary .pinions will effect the rotation of the ring 'n at the same speed as the pinion 0,, i. e. the said ring and pinion will have a fixed relative angular position iii-respectively of the rotation of the main shaft, but when the "ring 2 is rotated, this will give the ring a a speed different from 0,; in short upon rotating the ring 2 by a certain number of teeth realtively to 2 this will rotate 11. by the same number of teeth relatively to e so, that the socket z' may be turned to a known degree relatively to the main shaft, and this will control the distance-between the disks 0 and c and hence the ratio of the speeds. Back m0t2'0n.As above stated, the apparatus allows of rotating the actuated shaft at speeds which can be varied in a continuous manner between 1 and 1/4; the speed of the driving shaft, and in the contrary direction to the latter. For motor car use, the said change-speed device may therefore be employed for the forward motion, by disposing the differential pinions in the inverse direction relatively towhat is employed in the known devices.

For the back motion, I may mount upo the difierential (Fig. 13)-providedwith the tapered toothed ring 0 known per sea second toothed ring 0", and by means of an. eccentric e actuated by the lever Z the small controlling pinion 0 may be laterally moved whereby it will engage with either ring as desired, and this will provide for the rotation of the vehicle axle in either direction, but this arrangement would require a control extending as far as the rear axle.

' Two other arrangements may be adapted, as follows: a

1. Semi-direct engagement.During the forward motion, the actuated shaftof the change-speed device engages the shaft of the universal joint device ,(Cardan shaft) and drives the latter by a mechanism which is interposed but which forms a unit during this forward'motion. For this purpose I may employ the device shown by way of example in Fig. 14 in partial lengthwise section and in Fig. 15 in cross section, it

being placed between the shaft 1" extending from the change-speed box and the shaft 1' proceeding to the Cardan device, wherein a pinion p keyed to the end of the actuated shaft 9" engages the two planetary pliiions p p loosely mounted on the disk q which is provided with a female clutch cone. 1

The said disk is revoluble on the socket d and may be'secured to the toothed disk C so as to actuate-through the medium of the frictioncone mF-the shaft r carrying the said cone. The cone m is keyed so as to rotate with the disk C, but is laterally slidable by means of the two rollers m which are controlled by the fork g in such manner as to enter into fixed .contact with the disk g. Theaggregate r p p p gmC T will thus form a unit turning.

tionary casing c by means of the brake f which is controlled by the lever Z herein the shafts of the planetary pinions become stationary, and the pinions, actingas ordinary wheels, will'draw with them the disk C and the shaft 7 in the contrary direction to r and at a speed which is reduced in the ratio of. p to C ofg Thetwo operations of the fast holding by the cone m or by the brake f may be readilyobtained by the use of a single lever which acts through the medium of a pivoted bar upon the rod and link gear actuating the brake f and the fork g This arrangementv for simultaneous control, which may consist of known means and will'necessarily vary according to the case, has not been represented in order to avoid complication in they drawings.

2 Direct drive-It may be necessary' to provide for a direct drive, i. e. to actuate the Cardan shaft directly by the driving shaft.v $uch an arrangement is shown m longitudinal section in Fig. 16' and diacontinued at 0.

grammatically in cross section in Fig. 17. In these figures, the shaft a of 'Fig. '7 is To the shaft 0" is keyed the pinion p engaging two pinions p 15''- mounted on. the stationary casing c and transmitting -in the inverse direction-the rotation, of the shaft 1' to the toothed disk C which is provided. with the claws ft coacting through the medium of the sleeve 9 (controlled by the fork M) with the like claws f on the sleeve. gflithereby imparting the reversed and reduced motion ofthe shaft r to the shaft 1*. This case corres nds to the forward motion when-it isesired to use the range of speeds shown in :Figs. 7 to 12.

, To the toothed diskG is keyed a pinion I 9 adapted to actuate-through the medium of two 'pinions q? and g casing e -a toothed disk 8 which loose in the-said casing; the sari disk carries thei v .ingthe speed ratio, as herembefore set forth.

mounted in. the

claws 7" which can be brought intoien age- :ment' with like claws f? on the sliding s eeve g3, thustransmitting the motion of the disk C (reversed and reduced) to the shaft r' I '6 l aid .T 1eeve with .thelikeclawsf disposed This case corresponds to theback motion.

Finally, vby.iengagmgthe claws f of the 1 the discs 2 trary directions.

on the end a of the shaft a, I directly transmit the motion, of the driving shaft a to the shaft 7 Herein the direct drive serves only for the maximum speed.

Obviously, the rollers .13 may have any (Fig. 19) a cylindrical shape (Fig. 20) or the like. But such shapes appear to be less advantageous than that ofthe double cone, and particularly, the cylindrical shape will not allow a speed ratio of unity; the

spherical shape, while it provides for the I constant value of a coefficient which has Lil some importance in the designing of the apparatus, will diminish the efficiency for certain speed ratios. 'And the efficiency isto be considered as of particular importance in thisclass of apparatus.

Ulimigc-spced device with automatic contrcZ (Fig. v21).---Fi'g. 21 again shows the driving shaft a, the collar 2' the toothed rings n and 6 the planetary pinions y and the tangent screw mounted on the shaft g (Fig. 7).

The

shaft 9 instead of beingcontrolled by the driver himself in either direction, inorder to vary the speed ratios, is herein under automatic control. To obtain this result, the driving shaft 0 carries two bevel gears 5 and 6 engaging the respective bevel gears 7 and 8, and it Wlll be observed in Fig. 22 that, due to their.

disposition, the latter pinions rotate in con- The pinion 7 is keyed to a shaft 9 extending through thehollow shaft 10 of the pinion 8; theshaft 911% secured to its end a female cone 11, and the shaft 10 carries the female cone 12; these,

two cones are mounted opposite each other, and have between them a double male cone 13, 14 which is coaxial with the shaft 9 but is rotatable thereon as well as movable lengthwise. The tapered member 13 14 is secured to a casing 15 which iscentered in a ball bearing 16 and is urged at its left hand end by the spring 17 which .ab uts against an adjustable tappet 18. The aggregate-consisting of the casing 15 and-thetapered member 13-14will thus be urged to the right by the said spring which W1 I tend to bring it into contact with the interior of the female come 12. Upon the casing15 is mounted the toothedsleeve 19 whose teeth 20 engage the teeth of the gear wheel 21 which is keyed to the shaft 9 the he two heavy masses 22 and: 23 acting by centrifugal force are pivoted to the respect-i'v'e axles 24 and 25 which are'jmounted latter serves to control the device for changspring 17 and to the left by'the centrifugal effect of the said masses.

In the following considerations, the term standard speed signifies the speed for which the effect of the said spring exactly counterbalances the centrifugal effect of the said masses, and herein the tapered member '1314 will be in the position of equilibrium between the two female cones 11 and 12, and without contact with either; it will therefore be unable to rotate, since the tangent screw f is irreversible.

Let it be supposed that the speed of the driving s'haft a becomes slower for any reason; the-effect of the said spring will now exceed the centrifugal effect of the said masses, sothat the cone 14 will come into contact with the female cone 12 and will be rotated by the latter, and this will effect the rotation of the casing 15 and its toothed sleeve 19, so that the latter will rotate the pinion 21 and the shaft '9 through the medium of the toothed portion 20.

I have already set forth the manner in which the shaft 9 acts through the medium of the tangent screw 7, the planetary pinions e 3 and thetoothed ring 11?, upon the member'i, and finally changes the speed ratio (Fig. 7).

In order that the said apparatus shall operate in the proper manner, it is simply necessary that the person skilled in the art shall take due care that the direction of rotation of the pinion 8 and the cone 12, as also the direction of the threads of the screw f shall be such that in the last-mentioned example, the control action shall reduce the speed of the actuated shaft relatively to the speed of the driving shaft g.

In these conditions, should the load on the engine be reduced, the speed of the engine will rise to the point at which the centrifugal force of the saidmasses, increasing with the speed, will counterbalance the efiect of the'said spring, thus bringing the tapered member 13.14 into the middle position the latter will then no longer be actuated by the female cone 12, and it will cease to rotate, as also the parts which it actuates, together with the shaft 9 The speed ratio of the apparatus will therefore remain at this new value, while the engine has now returned to the standard speed.

Should the speed of the. engine exceed the standard rate for any reason, the centrifugal force of the said masses will now overcome the action of the said spring, and the cone 13 will coact at the leftwith the interior of the female cone 11, so that the latter will now actuate the aggregate comprising the cones 13 and 14, the sleeve 15, the sleeve 19, the teeth 20, the gear wheel 21', the shaft g, the worm and the toothed ring 2. As above stated, the cone 11 rotates in the contrary direction with respectto the cone 12, so that theparts will be rotated by the cone 11 in the inverse direction to what takes place when they are rotated by the cone 12, i. e. the speed of the actuated shaft will exceed that of the driving shaft. The engine is thus braked to a greater degree, and will be slowed down; the centrifugal force of the said masses will hence diminish until it is counterbalanced by the action of the said spring, at which time the tapered member 13-14 will resume its position of equilibrium and the apparatus will become inoperative.

It will thus he observed that in virtue of its action upon the change of speed, my said mechanism will constantly restore the engine to the standard speed. To determine this ,standard speed as the driver may desire, the stop or tappet 18 for the spring 17 should be adjustable at will: it may for instance be controlled by a fork 31 actuated by a handle 32 which may be set in various positions, for example upon the quadrant 33. It will he simply necessary, for the driver to set the handle in the position cor-responding to the speed which he may desire, and the engine will be constantly brought back to this speed in an automatic manner. If the handle 32 is pushed to the left, the said fork will move to the right, thus compressing the spring. and in order to overcome the action of the spring, the centrifugal action of the'said masses must be increased. Otherwise stated. the standard speed of the engine increased according as the handle is moved to the left. and inversely, the standard speed decreases for the right hand motion of the handle.

It should however be noted that in certain cases, the member i may attain its extreme position in one or the other direction, while at the same time the extreme ratio of the speeds (maximum or minimum) will not sutiice to correct the racing or the slowing of the eng ne. In this event, the cone which is in friction contact will continue to act. even though the member 71 is at the end of its stroke, and the mechanism would thus become broken.

To obviate this drawback, the member 2 may be provided with a stud ll which. somewhat before the said member attains the end of its stroke, will,abu-t in either direction against a projection 35 disposed on a sliding member 36 which actuates the rod 37 and the rocking lever 38 whereof the outer end controls-by the fork 39the sleeve 40 which moves together with the sleeve 19 and hence together with the cones 13 and 14, in the lengthwise direction. Should the member 2 turn through more than one revolution, it will 1 suliice to interpose between the said member and the projection 35 a reduction gearing device carrying the stud 34 (not shown).

Obviously, the several elements should be so disposed as to act in the proper direction. .For instance, with the shaft a rotating according to the arrow (Fig. 21) the pinion 7 will rotate according tothe arrow Fig.- 22, and the pinion 8 will rotate in the contrary direction as well as the cone 14 and the sleeves 15 and 19 connected therewith; the shaft 9 will then rotate according to the 1 arrow Fig. 21, and the worm f will rotate the member a in the clockwise direction.

Should the action of the speed ratio changing device prove insufiicient to allow the en gine to resume its stand'ard'speed, the. stud 34 will abut against the left hand face of the projection 35, thus driving it to the right, and (by means of the lever 3a) the socket withthe sockets 19 and 15 will be moved to the left, as well as the cone 14 which is thus uncoupled and its action stopped without the intervention of the centrifugal device 2223. In the eventof racing of the engine which it is impossible to prevent, the action will be thesamebut in the contrary direction.

Obviously, the details of construction here.

inbefore set forth byway of example will not limit the scope ofrmy said invention, and for instance the double clutching device may be replaced by adouble coupling of varia le construction, or like means'may be adopted. It is evident that the stud 34, the projection 35,the sliding member 36, the rod 37 and the lower part of the lever 38 are shown in Fig. 21 to the rear of the plane of the section, and the drawing is somewhat of a diagrammatic nature in order to avoid the use ofanother figure whereby the description would be complicated.

What I claim is I 1. A progressive change-speed device comprising a driving shaft, an actuated vshaft, rollers having a symmetrical shape relatively to their e uatorial lane, two pairs of disks upon whic the said rollers are adapted to roll withoutescaping in.sliding, means for,'angularly connecting together the. disks of a given pair, 'meansconnecting angularly one of the two pairs of disks with the driving shaft, an irreversible mechanism for the positive control of the longitudinal spacing between the pair of disks connected with the driving shaft, two helical ramps connecting the disks of the other pair with the actuated shaft and constantly urging the said disks against the-rollers with a suitable pressure,

a spring interposed between the two disks which are connected with the actuated shaft and urging them together even when there is no motion nor opposing couples.

- 2. A progressive change-speed device comof the twopairs of disks with the driving shaft, an irreversible mechanism for the positive control of the longitudinal spacing between the pair of disks connected with the drivingshaft, two helical ramps connecting the disks'of the other pair wi'ththje actuated shaft and constantly urging the said disks against the rollers with a suitable pressure,

"a spring interposed between the two diskswhich are connected with the actuated shaft and urging them together even when there is no motion nor opposing couples.

3. A progressive change-speed device comprising a driving shaft, an actuated shaft,

four rollers at the minimum which have the symmetrical position about the said driving shaft and have a symmetrical shape relatively to their e uatorial plane, two pairs of disks upon whic the said rollers are adapt ed to roll without escaping in sliding, an irreversible nut with right and left hand thread which is angularly connected with the driving shaft and is screwed to the disks of one of the two pairs, means for the un ular setting of the said nut upon the driving a shaft," two helical ramps connecting the disks'of the other pair with the actuated shaft and constantly urging the said disks against the rollers with a suitable pressure,

:1 spring interposed between the two disks WlllChflIG connected with the actuated shaft and urging them together even when there is no motion nor opposing couples. y

4. A progressive change speed device comprising a driving shaft, an actuated shaft,

four rollers at the minimum which have the symmetrical position about the aiis of the said driving shaft and have a symmetrical shape relatively to their equatorial plane, pivoted brackets supporting the saidrollers, two pairs of disks formed by surfaces of revolution, and upon which the said rollers areadapted toroll without escaping in sliding an irreversiblenut with right and left hand thread which is angularly connected with; the driving shaft and is screwed to the two disks of a given pair, means for the angular setting of the nut upon the driving shaft, 1 two helical ramps connecting T the disk'sj gni the other pair with the actuated shaftfand constantly urging the said disks the rollers with a suitable pressure,asp;ring,inj.

nemeu s e terposed between the two dis which we connected with the aetua shaft and urgg them'together even when there isno mo tion nor opg 'conp1es.'

5., A progrve ehange-sp devicecomprising a hollow actuated sit, a driv shaft traversing the whole meeha, means for the direct couple 0f the two shafts,v rollers which have a 'syetrieeli shape relatively to their equatorial lane, two pairs of disks upon wch the sei roiiers are adapted to roll without. escaping sliding meen sffor angmierly connecting 'together the dish of a given air, means eonnecting singularly oneof t e two pairs of disks with the driving sheit, means eoeet;

:41 the other pair of disks'with the actuated. shaft, and means for valgiying.

the longitudinal distance between the of a given pair. In testimony whereof I have signed i specification. A-

' J ROBERTESNAULTfELTERIEi 

